Note : Les descriptions sont présentées dans la langue officielle dans laquelle elles ont été soumises.
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MAGNETICALLY COUPLED SEALLESS CENTRIFUGAL PUMP
BACKGROUND OF THE INVENTION
The field of the present invention is pumps which are magnetically
engaged.
Pumps that utilize an open/semi-open impeller need a means to adjust
the impeller axially relative to the pump case. As the impeller and case wear
over time, the clearance between the impeller and the case opens up. This
degrades performance; the pump efficiency decreases; and the produced pump
pressure can decrease. The impeller is then set to the appropriate clearance
from the case during each maintenance cycle, using the external provisions of
the pump, thereby not requiring the pump to be taken out of service. The
concept of having a rotor that is externally adjustable is industry standard
for
normal sealed pumps. The mechanisms accompanying axial adjustment in a
sealed pump are generally located in the power frame. This is possible with a
sealed pump because the impeller is mechanically connected to the ball
bearings (in the power frame) through the shaft, etc.
Other features are commonly employed. Shunted process fluid is
frequently used for lubrication of bearing surfaces. In magnetically coupled
sealless pumps, the bearing surfaces and the interior magnets of the magnetic
coupling conventionally are wetted, while the exterior magnets are in
atmosphere. Such arrangements require bearing and magnetic mountings on
multiple elements.
Rub rings are commonly employed with a component to restrict eccentric
rotation upon catastrophic bearing failure. Such rotation can damage sealing
canisters. Plates are also used to protect workers from catastrophic component
failure. Often, component complexity in arranging these and other details is
dictated in magnetically coupled pumps by the pump drive being concentrically
outwardly of the driven rotor assembly, usually including an impeller shaft.
Date Recue/Date Received 2020-11-02
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SUMMARY OF THE INVENTION
The present invention is directed to a magnetically driven centrifugal pump
including a pump case, an impeller, a stuffing box and magnetic coupling
between
an impeller rotor and a drive. A canister extends through the magnetic
coupling to
form a barrier between the impeller rotor side and the drive side of a pump.
In a first separate aspect of the present invention, the stuffing box includes
a stuffing box outer fixed to the pump case and a stuffing box inner
threadedly
engaged with the stuffing box outer about the axis of impeller rotation. The
impeller
rotor is axially fixed relative to the stuffing box inner. Rotation of the
stuffing box
inner relative to the stuffing box outer can then adjust the impeller
clearance in the
pump case.
In a second separate aspect of the present invention, an annular rotor
bushing is between the rotor and the stuffing box inner; an annular impeller
bushing
is between the impeller hub and the stuffing box inner and two opposed thrust
bushings are between the stuffing box inner and the rotor. All may be mounted
exterior to the drive. This common access simplifies the stuffing box and
facilitates
ease of service.
In a third separate aspect of the present invention, the drive is fixed
relative
to the pump case and includes a drive output. A rub ring is mounted to the
stuffing
box and extends inwardly to circumferentially surround the drive output to
protect
the canister. The rub ring closes the end of the stuffing box around the drive
output
by extending inwardly from a periphery of the stuffing box.
In a fourth separate aspect of the present invention, a process fluid shunt
extends in seriatim through the annular impeller bushing, a first of the
thrust
bushings, the annular rotor bushing, a second of the thrust bushings and the
magnetic coupling outwardly of the canister. The arrangement provides further
component simplification.
The foregoing separate aspects are contemplated to also be employed in
combination with one another. Accordingly, it is an object of the present
invention
to provide an improved magnetically coupled centrifugal pump. Other and
further
objects and advantages will appear hereinafter.
Date Recue/Date Received 2020-11-02
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BRIEF DESCRIPTION OF THE DRAWINGS
Figure 1 is a cross-sectional elevation of a magnetically driven centrifugal
pump taken through the axis of impeller rotation;
Figure 2 is a cross-sectional detail of the stuffing box illustrated in Figure
1;
Figure 3 is a detail of the magnets and bushings in the stuffing box of Figure
2;
Figure 4 is a cross-sectional elevation of a second embodiment of a
magnetically driven centrifugal pump taken through the axis of impeller
rotation;
Figure 5 is a cross-sectional detail of the stuffing box illustrated in Figure
4;
and
Figure 6 is a detail of the magnets and bushings in the stuffing box of Figure
5.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
Turning in detail to the drawings, the Figures each show the surface of
sections through the axis of impeller rotation 10. The major components except
for
the pump case and the pump housing, which are asymmetrical because of volutes
and mountings, respectively, are substantially symmetrical about the axis of
impeller rotation. The first embodiment, Figures 1 through 3, differ from the
second
embodiment, Figures 4 through 6, by the support arrangements for the impeller.
In
both embodiments, a bushing is about the hub of the impeller to securely
support
the rotatable impeller.
A pump case 12 defining an impeller cavity and a volute is further defined by
a housing structure 13. The pump case 12 surrounds an open vane impeller 14
while the housing structure 13 extends over a stuffing box 16. The impeller 14
includes an impeller hub 15 extending away from the vanes of the impeller 14.
The
pump case 12 and housing structure 13 are conventionally assembled with bolts.
The housing structure 13 is shown in this instance to have an open arrangement
with holes about the circumference.
The stuffing box 16 includes a stuffing box outer 18 which is a collar with an
outer flange 19 engaging the pump case 12 and held in place by the housing
structure 13. The stuffing box 16 further includes a stuffing box inner 20
engaged
with the stuffing box outer 18 at a threaded engagement 22. The threaded
Date Recue/Date Received 2020-11-02
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engagement 22 provides for the stuffing box inner 20 to be rotated relative to
the
stuffing box outer 18 to allow axial translation of the stuffing box inner 20
relative to
the stuffing box outer 18 and in turn the pump case 12. After the desired
axial
position of the stuffing box inner 20 is achieved, the rotational position of
the stuffing
box inner can either be held by thread friction or by an external set screw.
The
stuffing box inner 20 extends from the threaded engagement 22 as a cylinder to
a
stuffing box inner detachable cap 24. The stuffing box inner detachable cap 24
is
held in place by fasteners.
A rotor 26 is located within the annular cavity defined within the stuffing
box
inner 20. The rotor 26 is also cylindrical with a front wall. A mounting hub
27 fixed
on the cylindrical front wall threadedly engages the impeller hub 15 so that
the
impeller 14 is detachably fixed to the rotor 26. With the rotor 26 located in
the
annular cavity with thrust bushings described below, the rotor 26 moves
axially with
the stuffing box inner 20 relative to the stuffing box outer 18. With the
stuffing box
outer 18 engaging the pump case 12 and the rotor 26 being engaged through the
mounting hub 27 with the impeller hub 15, the axial adjustment of the stuffing
box
inner 20 relative to the stuffing box outer 18 is used to create an
appropriate
clearance between the impeller 14 and the pump case 12.
A drive 28 is arranged inwardly of the rotor 26. The drive 28 includes a drive
output 29 that is cylindrical with an engagement to receive a drive shaft
coupled
with a motor (not shown) for torque transfer. The drive further includes a
drive shaft
power frame 30 with a shaft conventionally arranged in with bearings as shown
to
transfer rotary power from the motor. The housing is conventionally coupled
with
the housing structure 13 by bolts.
Power to the rotor 26 from the drive 28 is transmitted through a magnetic
coupling 31. The magnetic coupling 31 is traditional including driving magnets
32
associated with the drive 28 and driven magnets 34 associated with the rotor
26. A
canister 36 extends through the magnetic coupling. The canister 36 is
integrally
formed with the stuffing box inner detachable cap 24. The stuffing box inner
detachable cap 24 and the associated canister 36 are retained by fasteners at
the
end of the stuffing box inner 20. Thus, the canister 36 does not rotate with
either
the rotor 26 or the drive 28 but remains stationary in the pump unless the
impeller
14 is being axially adjusted. The canister 36 includes a concave end which
results
Date Recue/Date Received 2020-11-02
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in less distortion of the canister 36 under pressure loads from the pump
process
fluids.
In the preferred embodiment, the rotating components within the stuffing box
16 are mounted through bushings. The bushings used in these embodiments are
bushing pairs each with a static bushing associated with the stuffing box
inner 20
and a dynamic bushing each associated with the rotor/impeller assembly 26/14.
These components are held in place by conventional means. An annular rotor
bushing 38 is located between the stuffing box inner 20 and the rotor 26. The
annular impeller bushing 40 is between the stuffing box inner 20 and the
impeller
hub 15. In the first embodiment as illustrated in Figures 1 through 3, the
mounting
hub 27 includes an outer ring 41. The annular impeller bushing 40 is engaged
with
the mounting hub 27. This arrangement thus allows engagement of all of the
bushings with the rotor 26. At the same time, the annular impeller bushing 40
remains between the stuffing box inner 20 and the impeller hub 15 to
positively
mount the impeller 14. In the second embodiment, as seen in Figures 4 through
6,
the bushing 48 directly engages the impeller hub 15 to the same end. With
either
arrangement, the rotor 26 is rotationally mounted by the annular rotor bushing
38
and the annular impeller bushing 40 within the stuffing box inner 20.
A forward thrust bushing 42 is arranged between the stuffing box inner
detachable cap 24 and the rotor 26. A rearward thrust bushing 44 is located
between the stuffing box wall 25 and the rotor 26. The thrust bushings 42, 44
thus
retain the rotor 26 fixed axially within the stuffing box inner 20. Again, all
of the
annular and thrust bushings are traditionally placed within the pump.
A process fluid shunt 46 lubricates the bushings located about the rotor. A
.. shunt inlet 48 is located outwardly of the impeller hub 15 to extend
through the
annular impeller bushing 40. A gap between the rotor 26 and the stuffing box
wall
25 directs process fluid through the rearward thrust bushing 44. An annular
gap
between the stuffing box inner 20 and the rotor 26 then permits the shunted
process
fluid to move to and through the annular rotor bushing 38. An annular cavity
adjacent the annular rotor bushing 38 defined in the stuffing box inner
detachable
cap 24 then directs the shunted process fluid through the forward thrust
bushing
42. The shunted process fluid is then released to around the canister 36 where
it
passes by the wetted magnets 34 and then to the shunt return 50 along the axis
of
Date Recue/Date Received 2020-11-02
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impeller rotation 10. The shunt inlet 48 is located outwardly on the open vane
impeller 14 of the shunt return 50 located along the axis of impeller rotation
10.
Thus, rotation of the impeller 14 is able to drive circulation of the shunted
process
fluid.
A rub ring 52 closes the drive end of the stuffing box inner 20 by extending
inwardly to the drive 28. In addition to closing the stuffing box inner 20,
the rub ring
52 is associated with a circumferential ring 54 located on the drive 28. The
maximum compressive deformation in the ring 54 is less than the gap between
the
canister 36 and either of the magnet assemblies 32, 34. This prevents damage
to
the canister 36 by catastrophic failure of any of the bearings.
Date Recue/Date Received 2020-11-02
